A three parameter viscous damper and isolator

Abstract: A vibration isolation apparatus includes a shaft (16) having a first and second end (18, 20). A piston (30) having an axial bore is coaxially positioned with the shaft to provide a damping passage (32) between the piston and the shaft. A flange (34) extends radially from the piston for coupling the apparatus to a load. A first extension (22) is coupled to and extends radially from the first end of the shaft and a second extension (24) is coupled to and extends radially from the second end of the shaft. Primary bellows (50, 52) extending from and secondary fluid paths (26, 28) extending through the first and second extensions (22, 24) provide a first volumetric stiffness in series with the damper. Secondary bellows (42, 44) connect the flange (34) to the first and second extensions (22, 24) and are coaxial with the shaft to provide a second volumetric stiffness parallel with the damper and the first volumetric stiffness.

Description: The present invention relates to the field of vibration damping and isolation. More particularly, the present invention discloses a three parameter viscous damper and isolation system. Precision structural systems carrying a load, such as a telescopic system, are susceptible to disturbances that can produce structural vibrations. Such vibrations may be contributed to the system by components or assemblies of the precision structural systems itself, for example, reaction wheel assemblies of the telescopic system. Since such precision structures tend to have little inherent damping, these vibrations can lead to serious performance degradation. Therefore, an efficient means of damping and isolating the load carried by the precision structures in a controlled manner is of considerable importance. Both active and passive damping and isolation techniques have been utilized. However, active systems suffer from high cost, low reliability and poor low level threshold performance. On the other hand, passive systems require no power, are often less expensive than active devices and do not drive the structure unstable. Thus, passive damping systems have proven to play a significant role in the overall design of precision structural systems. One such manner of implementing a passive system includes the use of viscous damping and isolation. Viscous dampers and isolators include a fluid reservoir sealed in a damping structure which utilizes viscous fluid shear forces to provide damping and isolation. One type of viscous damper and isolator, a conventional two parameter system 10, is shown in the mechanical schematic of Figure 1A. The system includes a damper with a damping function C A which could be implemented with a piston moving through a liquid in a cylinder. As the piston moves, the damping function is controlled by the size of an orifice allowing liquid to pass from one side of the piston to the other side of the piston. The orifice may be the clearance between the piston and the cylinder. The schematic two parameter system 10 also includes a spring K A , representing a spring constant. This spring K A is parallel with the damper C A and a mass M is attached and applied thereto. An implemented two parameter system is shown and described in US-A 4,760,996 corresponding to EP-A 0 339 113 and in US-A 3,980,358. An additional two-parameter system is described in the paper entitled, "A MultiAxis Isolation System for the French Earth Observation Satellite's Magnetic Bearing Reaction Wheel," by D. Cunningham, P. Davis and F. Schmitt, Proceedings of the ADPA/AIAA/ASME/SPIE Conference on Active Materials and Adaptive Structures, November 5-7, 1991. The paper describes a six degree of freedom isolation system using viscous dampers. EP-A 0 414 508 describes a two parameter vibration damping device comprising two cylindrical and flexible membrane members having one end portion of each membrane member connected to respective end portions of a piston and having another end portion of each membrane member connected to a respective face plate so as to form a closed chamber such that folded portions of both cylindrical and flexible membrane members face each other. A shaft projects through a bore in said piston constituting a restricted passage. The closed chamber is filled with a fluid which can flow from one membrane chamber to the other through said restricted passage. A mechanical schematic of an additional damper and isolator is shown by the three parameter system 12 of Figure 1B. The three parameter system 12, includes a spring K B , representative of a spring constant, in series with a damper C A representative of a damping function. The three parameter system further includes a spring K A representative of a spring constant, parallel to the damper C A and spring K B . A mass M or load is applied to the system. Such a mechanical schematic is discussed in the textbook entitled "Mechanical Vibrations Theory and Applications , F.S. Tse, I.E. Morse, R.T. Hinkle, Second Edition 1978, pages 106-107. It can be said that a two parameter system is simply a special case of a more general three parameter system; that is, when K B is equal to infinity. Most practical isolation systems have a finite value of K B due to some compressibility of the fluid or volumetric compliance in the housing of a particular viscous isolator. Nevertheless, they essentially act as a two parameter system because of the relatively large value of K B compared to K A ; K A being the stiffness in parallel with the damper C A . One of the prime concerns in the field of vibration isolation is the proper use of isolators to isolate loads from external vibrations under various load configurations with respect to a desired natural frequency. The natural frequency is the frequency at which a freely vibrating mass system oscillates once it has been deflected. In the case where external vibrations occur over a wide frequency range, resonance is said to exist when the natural frequency of the viscous isolator coincides with the frequency of the external vibration or excitation forces. Resonance causes magnification of the external vibration and may be harmful to the isolated structure if not controlled within reasonable limits. Two parameter systems lack adequate performance when isolation at frequencies substantially above resonance is important, and/or when reduced amplification at resonance is important as is shown by the transmissibility plot 200 of Figure 1C. The transmissibility plot 200 shows two dashed curves 204 and 202 representing two parameter systems of transmissibility versus frequency ratio, i.e., frequency of external vibrations to a natural frequency. Dashed line 202 represents a 50% damped system and shows that isolation at high frequencies is extremely poor. Dashed line 204 represents a 0% damped system and although isolation is much better at high frequencies, amplification at resonance is unacceptable. The three solid curves 206, 208 and 210 represent transmissibility versus frequency ratio for a three parameter system. As is shown, with a 100% damped system at resonance, the amplification at resonance is approximately a factor of 4. The same as for a two parameter 50% damped system. As shown by solid line curves 206 and 208, although isolation at high frequency is improved with a lesser damped three parameter system, i.e., curve 206 a 20% damped system and curve 208 a 50% damped system, amplification at resonance also increases. This indicates that a fundamental rule generally exists when optimizing a three parameter system; the rule being that the frequency at which maximum damping occurs should be equal to the resonance frequency. However, other basis of optimization may be more appropriate depending on the application. As is shown in Figure 1C, a three parameter system has the primary advantage over the two parameter system in that three parameter system provides better isolation at high frequencies with equal or less amplification at the resonance frequency. Although prior modeling of two and three parameter systems indicates that a three parameter system provides better isolation at high frequencies with equal or less amplification at the resonance frequency, an efficient three parameter viscous isolator providing such isolation is not known. Therefore, a need for such a three parameter viscous isolation system exists. SUMMARY OF THE INVENTION The invention as characterized in the independent claims discloses a vibration damping and isolation apparatus implementing a three parameter system to provide improved isolation at high frequencies with equal or less amplification at the resonance frequency than a two parameter system. The vibration isolation apparatus includes a shaft having an axis therethrough. The shaft has a first and second end. A piston having an axial bore is coaxially positioned with said shaft to provide a damper by forming a damping passage therebetween. The piston has a flange extending radially therefrom for coupling the apparatus to a load. A first extension is coupled to and extends radially from the first end of the shaft and a second extension is coupled to and extends radially from the second end of the shaft. Secondary isolation means extends from and through the first and second extensions for providing a first volumetric stiffness in series with the damper. Primary isolation means connects the flange to the first extension and second extension and is coaxial with the shaft for providing a second volumetric stiffness parallel with the damper and the secondary isolation means. Preferred details and embodiments of the invention are described in the dependent claims. In one embodiment of the invention, the first volumetric stiffness is less than about fifty times the second volumetric stiffness. Preferably, the first volumetric stiffness is at least equal to the second volumetric stiffness but no greater than about ten times the second volumetric stiffness. In another embodiment of the invention, the primary isolation means includes a first primary bellows connected between the first extension and the flange for forming a first fluid chamber and a second primary bellows connected between the second extension and the flange for forming a second fluid chamber. The first fluid chamber is connected to the second fluid chamber by the damping passage. The second isolation means includes a first fluid path through the first extension and a second fluid path through the second extension. The second isolation means further includes first secondary bellows connected to the first extension and a first sealing member to form a third fluid chamber. The third fluid chamber is connected to the first fluid chamber by the first fluid path. In addition, a second secondary bellows is connected to the second extension and a second sealing member to form a fourth fluid chamber. The fourth fluid chamber is connected to the second fluid chamber by the second fluid path. In additional embodiments of the invention, the damping passage has a greater resistance to flow than the first and second fluid paths. Also, the vibration isolation apparatus includes means for protecting the apparatus against overload. The invention and preferred embodiments thereof will be described with reference to the drawings. BRIEF DESCRIPTION OF THE DRAWINGS Figure 1A and Figure 1B are mechanical schematics of a two and three parameter isolation system, respectively, and Figure 1C is a transmissibility comparison of the systems. Figure 2 is a cross-sectional view of a viscous isolator in accordance with the present invention taken at Line A-A of the viscous isolator of Figure 7. Figure 3 is a cross-sectional view of the viscous isolator of Figure 2 taken at Line B-B of the viscous isolator of Figure 7. Figure 4A and Figure 4B are a plan view and an end view, respectively, of a shield of the viscous isolator of Figure 2. Figure 5A and Figure 5B are a cross-sectional view taken at Line A-A of Figure 7 and an end view, respectively, of a cover of the isolator of Figure 2. Figure 6 is a side view of the viscous isolator in accordance with the present invention. Figure 7 is a top view of the isolator as shown in Figure 6. Figure 8 is an end view of the isolator shown in Figure 6. Figure 9 is a cross-sectional view of an alternative embodiment of a viscous isolator in accordance with the present invention. Figure 10 is a cross-sectional view of an alternative embodiment for forming the secondary fluid chambers of a viscous isolator in accordance with the present invention. DESCRIPTION OF THE PREFERRED EMBODIMENT As described above with regard to the mechanical schematic two parameter and three parameter vibration isolation systems shown in Figure 1A and Figure 1B the three parameter system provides better isolation at high frequencies with equal or less amplification at resonance frequency than does a two parameter system. For example, with reference to the comparison transmissibility plot of Figure 1C, a two parameter system having 50% damping function has amplification at resonance of approximately 4-to-1 and attenuation at 100 Hertz of approximately -40db. In comparison, amplification at resonance for a three parameter system having a damping function at its maximum, may also be about 4-to-1; however, the attenuation at 100 Hertz is about -68db. The spring K B , in series with the damper C A , is the difference between the two and three parameter systems. Although as previously indicated, the two parameter system is simply a special case of the general three parameter system, i.e., when K B is equal to infinity, most isolation systems have a finite value of K B due to some compressibility of the fluid or volumetric compliance in the housing. Nevertheless, the isolation systems act essentially as two parameter systems because of the relatively large value of K B compared to K A ; K A being the stiffness that is in parallel with the damper and spring K B . A three parameter viscous isolator, utilizing an incompressible fluid such as silicone, in accordance with the present invention, provides a low value of K B as compared to K A in order to achieve a viscous isolator 14 which functions as a three parameter system rather than a two parameter system. Typical optimum values of K B range from K A to about ten times K A ; the values being a function of the frequency at which maximum damping is desired. When K B has a value of greater than about fifty K A , the three parameter system essentially functions for most applications as a two parameter system. The viscous isolator 14 in accordance with the present invention, i.e., functioning as a three parameter system, shall be described with reference to Figures 2-8. The viscous isolator 14 includes a shaft 16 having an axis 17 therethrough. The shaft 16 includes a first shaft end 18 and a second shaft end 20. Secured to shaft end 18 is a first extension 22 and secured to shaft end 20 is a second extension 24. As best shown in Figure 3, first extension 22 which is substantially the same as second extension 24, includes a plurality of secondary fluid paths 26 which extend through the extension 22. The first extension 22 also includes an opening 23 coaxial with axis 17 and sized to tightly secure shaft end 18 therein. In addition, the first extension includes a flange 66 for connection via hardware 68 to a base 64; such connection further described below. Positioned coaxial with the shaft 16 is piston 30. Piston 30 has an axial bore therethrough of a diameter greater than the diameter of the shaft 16 to form a primary damping annulus 32 therebetween. A flange 34 is integral with and extends radially from a midsection of piston 30. The flange 34 couples a load to the viscous isolator 14 via pivot flexure 40, tube 38 coupled to pivot flexture 40, and cover 36 coupled to tube 38 and to flange 34 via hardware 86. The cover 36 is shown in more detail in Figure 5A and Figure 5B. Cover 36 includes a main portion 78 for covering a portion of the viscous isolator 14, a tube mating portion 74 for coupling the cover to tube 38, a couple of voids 76 for allowing the flange 66 of extension 22 to connect to base 64, and a lip 72 for connection to the flange 34 through holes 80 via appropriate hardware 86. The cover is constructed of a suitable aluminum alloy. The flange 34 includes mating portions 37 for attaching a first primary bellows 42 and a second primary bellows 44 to a mating portion 27 of first extension 22 and a mating portion 29 of second extension 24, respectively. The mating portions 27, 29, 37 allow for attachment of the ends of the primary bellows 42, 44 thereto by an adequate sealing epoxy. The bellows described herein are constructed of nickel, a copper laminate, or any other suitable material and are available from Servometer Corporation, Cedar Grove, New Jersey, or MS BELOWS, Huntington Beach, California. The first primary bellows 42 has a first end connected to mating portion 37 of flange 34 and a second end connected to mating portion 27 of first extension 22 to form a first primary fluid chamber 46. The second primary bellows 44 has a first end connected to a mating portion 37 of flange 34 and a second end connected to a mating portion 29 of second extension 24 to form a second primary fluid chamber 48. The first and second primary fluid chambers 46, 48 are connected via the fluid passage of the primary damping annulus 32. The first and second primary bellows 42, 44 substantially provide the stiffness K A as shown in the mechanical schematic of the three parameter system 12 of Figure 1B. The damper C A as shown in the three parameter system 12 of Figure 1B is substantially provided by the shear forces of the incompressible fluid through the primary damping annulus 32. To complete the mechanical schematic of the three parameter system 12, as shown in Figure 1B, the viscous isolator 14 includes an additional pair of bellows, first secondary bellows 50 and second secondary bellows 52. To provide spring K B thereof first secondary bellows 50 is attached to a mating portion 27 of first extension 22 and to a first secondary sealing member 54 forming a first secondary fluid chamber 58. The first secondary fluid chamber 58 is coupled to first primary fluid chamber 46 by the secondary fluid path 26 which extends through the first extension 22, Figure 3. Likewise, the second secondary bellows 52 has a first end which is connected to a mating portion 29 of second extension 24 and a second secondary sealing member 56 to form a second secondary fluid chamber 60. The second secondary fluid chamber 60 is coupled to the second primary fluid chamber 48 via the secondary fluid path 28 through the second extension 24. In the preferred embodiment, as shown in Figure 2, the secondary bellows 50 are connected to a lip of the secondary sealing member 54 and the extension 22 to form the secondary fluid chamber between the inside of the bellows and a cylindrical body portion of the sealing member 54. Likewise, each of the secondary bellows may be connected in a compressive configuration as shown in Figure 10. The secondary bellows 50 are connected to a lip 170 extending from a cylindrical body portion 171 connected to the extension 22 and a seal plate 172 forming the secondary fluid chamber 58 between the outside of the bellows and the cylindrical body portion 171. The viscous isolator 14 is further provided with a base 64 for coupling the viscous isolator 14 to ground or an additional load. The base 64, best shown in Figures 6-8, includes a lower base portion 83 for attachment of the base to ground or a load via hardware 88. An upper base portion 81 integral and transverse to the lower base portion 83 connects flange 66 of extension 22 via hardware 84 to ground or load. Likewise, a flange of second extension 24 is connected to upper base portion 81 via hardware 82. In addition, a shield 62, shown in further detail in Figures 4A and 4B is attached also by hardware 82 to the upper base portion 81 of base 64 for bellows protection. The shield 62 is formed from a suitable aluminum alloy and includes a lip 70 having holes 71 therein for such connection. As described with reference to Figures 2-8, the viscous isolator 14 is a three parameter hermetically sealed isolator. The viscous isolator 14 has no sliding or rubbing elements that might wear or cause Coulomb friction or stiction. The primary damping annulus 32 is continually maintained by positioning piston 30 a predetermined distance from shaft 16 and maintaining that distance through the connections of the shaft ends 18, 20 to the first and second extensions 22, 24, respectively, and connection of the flange 34 via the primary bellows 42, 44 to the first and second extensions 22, 24, respectively. The stiffness of the primary bellows 42, 44 prevent such Coulomb friction or stiction. The essential functions of the three parameter viscous isolator 14 are provided by the first and second primary bellows 42, 44; the first and second secondary bellows 50, 52; the first and second sealing members 54, 56; the piston 30; the shaft 16; the primary damping annulus 32; the plurality of secondary fluid paths 26; and the incompressible fluid contained within the viscous isolator 14, all of which components are axially symmetric about axis 17. When a force is applied to the viscous isolator 14, motion takes place between the shaft 16 and the piston 30 causing fluid to flow from one of the primary fluid chambers 46, 48 to the other fluid chamber via the damping annulus 32. Fluid shear takes place in the primary damping annulus 32 providing system damping. Some fluid will also flow from the first and second primary fluid chambers 46, 48 through the first and second secondary fluid paths 26, 28 to the first and second secondary fluid chambers 58, 60. The resistance to flow through the secondary fluid paths 26, 28 is made small as compared to the primary damping annulus 32 to minimize damping by such secondary fluid paths 26, 28. For example, in the preferred embodiment the cross sectional area of the plurality of secondary fluid paths of one of the extensions 22, 24 is approximately 32 times as large as the cross sectional area of the damping annulus 32. The first and second secondary bellows 50, 52 and the associated first and second secondary fluid paths 26, 28, respectively, substantially reduce the volumetric stiffness K B , Figure 1B, of the viscous isolator 14. K B becomes essentially the axial stiffness of the secondary bellows. With the addition of the first and second secondary bellows 50 and 52, the designer of the viscous isolator gains the freedom to select a K B over a very large range by simply changing the design of the first and second secondary bellows 50,52. As previously indicated, the design of the secondary bellows is selected such that the volumetric stiffness K B is less than fifty times the volumetric stiffness K A in order to prevent the viscous isolator from functioning essentially as a two parameter system. Typically, the first and second secondary bellows 50, 52 are selected such that the volumetric stiffness K B is in the range of from K A to ten times K A . There are several ways for changing the design of the secondary bellows to meet such ratio requirements between the volumetric stiffness of K A and K B ; such designs not being limited to those listed below. Two particular methods are to change either the wall thickness of the bellows or the number of convolutions of the bellows. For example, in Figure 2, the viscous isolator 14 includes primary bellows having two convolutions and the secondary bellows 50, 52 having three convolutions. Likewise, in a preferred embodiment, the wall thickness of the primary bellows 42, 44 is about .00224 inches and the wall thickness of the secondary bellows 50,52 is about .00276. As will be recognized by one skilled in the art, such values change depending upon the design. One fundamental rule that is generally effective when optimizing a viscous isolator design is to set the frequency at which maximum damping occurs to be equal to the resonance frequency. However, other bases of optimization may be more appropriate depending on the application. Constant, however, is that the three parameter viscous isolator in accordance with the present invention substantially outperforms the two parameter system when isolation at frequencies substantially above resonance is important to the isolated system and/or when amplification at resonance is important. An alternative embodiment of the present invention is shown by the viscous isolator 100 of Figure 9. Viscous isolator 100 provides the essential functions of the three parameter system in much the same manner as viscous isolator 14 in that viscous isolator 100 includes shaft 101 having first and second shaft ends 102 and 103. A first and second extension 104, 106 are coupled to and extend radially from the first and second ends 102, 103 of shaft 101, respectively. A piston 112 having an axial bore of a diameter slightly larger than the diameter of the shaft 101 is positioned coaxial to the shaft 101. A damping passage 114 is provided between shaft 101 and piston 112. The piston 112 includes a flange 116 which extends radially from the mid-section of piston 112. A first and second primary bellows 118, 120 form first and second primary fluid chambers 122, 124, respectively, and first and second secondary bellows 126, 132 in conjunction with first and second sealing plates 128, 134 are coupled to first and second extensions 104, 106, respectively, to form first and second secondary fluid chambers 130, 136. The first and second extensions 104, 106 include first and second secondary fluid paths 108, 110 therethrough, respectively. As such, the elements of viscous isolator 100 substantially match those of viscous isolator 14 and provide the essential three parameter functions like that of viscous isolator 14. Viscous isolator 100 further includes a housing 156 which is connected to flange 116 for connecting force 162 via pivot flexture 158 to the viscous isolator 100. Likewise, the viscous isolator 100 includes an inner cover 144 connected to extension 104 for coupling a force 160 to the viscous isolator 100 via pivot flexture 154. A compressed gravity off load spring 142 is positioned between an inside surface 147 of inner cover 144 and flange 116 to add axial stiffness to the viscous isolator 100 to off load a load in a gravity environment; in the preferred embodiment the spring 142 can absorb about 150 pounds. An outer cover 146 connected to flange 116, provides a tension stop and gap 138 which is closed when no load is applied. In other words, surface 150 of inner cover 144 is in contact with surface 148 of outer cover 146 when no load is applied. In turn, compression stop and gap 140 would be double the size. The tension stop and gap 138 and compression stop and gap 140 are about equal when a desired and predetermined load is applied and no vibration exists. The compression stop and gap 140 protects the viscous isolator 100 against overload. Movement gap 152 allows inner cover 144 to move with respect to outer cover 146.

Claims: A vibration damping and isolation apparatus, comprising: a) a shaft (16; 101) having a first (18; 102) and second (20; 103) end; b) a piston (30; 112) having an axial bore coaxially positioned around said shaft (16; 101) to provide a damping passage (32; 114) therebetween, said piston having a flange (34; 116) extending radially therefrom for coupling the apparatus to a load; c) a first extension (22; 104) coupled to and extending radially from said first end (18; 102) of said shaft (16; 101); d) a second extension (24; 106) coupled to and extending radially from said second end (20; 103) of said shaft; and e) primary isolation means (50, 52; 126, 132) coaxially extending from said first (22; 104) and second (24; 106) extensions for providing a first volumetric stiffness in series with said damping passage (32; 114); characterized by f) secondary isolation means (42, 44; 118, 120) connecting said flange (34; 116) to said first extension (22; 104) and said second extension (24; 106) and coaxial with said shaft (16; 101) for providing a second volumetric stiffness in parallel with said damping passage (32; 114) and said primary isolation means (50, 52; 126, 132), said secondary isolation means (42, 44; 118, 120) connected to said primary isolation means (50, 52; 126, 132) via fluid paths (26, 28; 108, 110) through said first and second extensions (22, 24; 104, 106). The apparatus according to Claim 1, wherein said secondary isolation means (42, 44; 118, 120) includes: a) first bellows (42; 118) connected between said first extension (22; 104) and said flange (34; 116) for forming a first fluid chamber (46; 122); and b) second bellows (44; 120) connected between said second extension (24; 106) and said flange (34; 116) for forming a second fluid chamber (48; 124), said first fluid chamber connected to said second fluid chamber by said damping passage (32; 114). The apparatus according to Claim 1 or 2, characterized in that said primary isolation means (50, 52; 126, 132) includes: a) third bellows (50; 126) connected to said first extension (22; 104) and a first sealing member (54; 128) to form a third fluid chamber (58; 130), said third fluid chamber connected to said first fluid chamber (46; 122) by a first fluid path (26; 118) through said first extension (22, 104); and b) fourth bellows (52; 132) connected to said second extension (24; 106) and a second sealing member (56; 134) to form a fourth fluid chamber (60; 136), said fourth fluid chamber connected to said second fluid chamber (48; 124) by a second fluid path (28; 110) through said second extension (24; 106). The apparatus according to claim 3, characterized in that said third and fourth bellows (50, 52; 126, 132) include a predetermined wall thickness to tune the apparatus for optimum performance. The apparatus according to claim 2 or 3, characterized in that said bellows (42, 44; 50, 52; 118, 120; 126, 132) include a predetermined number of convolutions to tune the apparatus for optimum performance. The apparatus according to claim 5, characterized in that said predetermined number of convolutions and said predetermined wall thickness of said third and fourth secondary bellows (50, 52; 126, 132) are selected to set the frequency at which maximum damping occurs to be equal to a resonance frequency. The apparatus according to one of the claims 3 to 6, characterized in that said damping passage (32; 114) has a greater resistance to flow than said first and second fluid paths (26, 28; 108, 110). The apparatus according to one of the preceding claims, characterized by means (142) for protecting said apparatus against overload. The apparatus according to claim 8, characterized in that said protection means includes a preloaded spring (142) coupled to one of said extensions (104, 106) and said flange (116) for preloading said apparatus. The apparatus according to one of the preceding claims, characterized in that said first volumetric stiffness is less than about fifty times said second volumetric stiffness. The apparatus according to one of the preceding claims, characterized in that said first volumetric stiffness is at least equal to about said second volumetric stiffness but no greater than about ten times said second volumetric stiffness. The apparatus according to one of the preceding claims, characterized in that a distance (32; 114) between said axial bore of said piston (30; 112) and said shaft (16; 101) is continually maintained by said secondary isolation means (42, 44; 118, 120).

Inventors: CUNNINGHAM DAVID C, DAVIS LAWRENCE P, DUNCAN DAMON H, CUNNINGHAM, DAVID C., DAVIS, LAWRENCE P., DUNCAN, DAMON H.
Applicants: HONEYWELL INC, HONEYWELL INC.
Application year: 1994
Main classification: F16F9
IPC codes: F16F15, F16F13, F16F9